EP3223971A1 - Dispositif et procédé de refroidissement d'un rouleau - Google Patents

Dispositif et procédé de refroidissement d'un rouleau

Info

Publication number
EP3223971A1
EP3223971A1 EP15801169.2A EP15801169A EP3223971A1 EP 3223971 A1 EP3223971 A1 EP 3223971A1 EP 15801169 A EP15801169 A EP 15801169A EP 3223971 A1 EP3223971 A1 EP 3223971A1
Authority
EP
European Patent Office
Prior art keywords
cooling
roller
bearing
cooling shell
roll
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP15801169.2A
Other languages
German (de)
English (en)
Other versions
EP3223971B1 (fr
Inventor
Matthias Kipping
Johannes Alken
Ralf Seidel
Torsten Müller
Magnus TREUDE
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
SMS Group GmbH
Original Assignee
SMS Group GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by SMS Group GmbH filed Critical SMS Group GmbH
Publication of EP3223971A1 publication Critical patent/EP3223971A1/fr
Application granted granted Critical
Publication of EP3223971B1 publication Critical patent/EP3223971B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/06—Lubricating, cooling or heating rolls
    • B21B27/10—Lubricating, cooling or heating rolls externally
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B38/00—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product
    • B21B38/02—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring flatness or profile of strips
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B38/00—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product
    • B21B38/06—Methods or devices for measuring, detecting or monitoring specially adapted for metal-rolling mills, e.g. position detection, inspection of the product for measuring tension or compression
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01B—MEASURING LENGTH, THICKNESS OR SIMILAR LINEAR DIMENSIONS; MEASURING ANGLES; MEASURING AREAS; MEASURING IRREGULARITIES OF SURFACES OR CONTOURS
    • G01B3/00—Measuring instruments characterised by the use of mechanical techniques
    • G01B3/12—Measuring wheels
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/06—Lubricating, cooling or heating rolls
    • B21B27/10—Lubricating, cooling or heating rolls externally
    • B21B2027/103—Lubricating, cooling or heating rolls externally cooling externally

Definitions

  • the invention relates to an apparatus and a method for cooling a roll.
  • the roll can be a roll in a roll stand for rolling typically metallic rolling stock or a measuring roll.
  • the cooling of the roll takes place using a cooling shell attached to the roll.
  • the invention further relates to a rolling stand and a measuring device with such a device.
  • Devices for cooling a roll, in particular a roll, using a cooling shell are basically known in the art, such. From JP 63303609 A, DE 3616070 C2, DE 20 2010 202 340 A1, DE 10 2012 219 722 A1 and DE 10 2012 216 570 A1.
  • the first two publications disclose a cooling device with a cooling shell for realizing a forced convection for cooling the roll. Common to all cited documents is that in each case a fixed positioning of a cooling shell relative to the respective roller to be cooled and thus a fixed adjustment of the size of a cooling gap between the cooling shell and the surface of the roller to be cooled for carrying a coolant is provided.
  • the height or size of the cooling gap be adapted to changing environmental or process conditions.
  • the rolls are reground several times during their lifetime, with each roll cut typically requiring readjustment of the cooling gap.
  • the necessary adjustments to the known in the prior art cooling devices or adjusting devices for the cooling shells are made manually or semi-automatically via screws in the prior art. These settings must be made outside of the rolling stand, as this is not possible in the rolling mill due to space, time and danger reasons. It also seems questionable whether the said manual adjustments of the gap height in the rolling stand can be made at all with a required accuracy.
  • a disadvantage of the known from the prior art cooling devices, ie the cooling shells and their Anstellvorraumen is further that by their attachment to the chocks of the rollers on the one hand, the weight distribution between the inlet and the outlet for the rolling stock in a rolling mill is uneven and on the other hand, the rigidity of the overall system for a bend about the axis of rotation of the roller further increases, which adversely affects both the roll bending. This is disadvantageous for the friction and control behavior of the rolls. If the cooling medium at the end of the cooling gap between the cooling shell and the roller to be cooled can not leak freely or not without limitation, this is disadvantageous for the cooling effect.
  • the invention has the object of developing a known device and a known method for cooling a roller and a known rolling mill and a known measuring device with such a device to the effect that the size of the cooling gap, d. H. the radial distance between the cooling shell and the surface of the roll to be cooled, always automatically optimally adjusted during operation of the device.
  • This object is achieved with regard to the device by the subject of claim 1.
  • This is characterized in that the single bearing has a degree of freedom in the radial direction relative to the circular arc-shaped cross section of the cooling shell, so that the cooling shell is mounted freely displaceable in the bearing in the radial direction.
  • roller means, for example, a roll in a roll stand for rolling rolling stock or a measuring roll in a rolling mill processing plant
  • the single bearing can consist of several part bearings, in particular two halves, which all have the same axis of rotation.
  • the bearing may be formed as a spherical bearing to ensure a parallelism of pivot axis of the cooling shell and roller axis and thus the functionality of the device in this case, even in an inclined position of the roller.
  • the claimed free displacement of the cooling shell in the radial direction advantageously causes the size or height of the cooling gap between the inside of the cooling shell and the surface of the roll during the rolling operation depending on the volume flow or the pressure with which the cooling medium introduced into the cooling gap is set automatically, automatically or automatically according to a free game of forces automatically correct. This is on the one hand optimal in terms of the cooling effect to be achieved, because in particular no undesirable turbulence in the flow of the cooling medium in the cooling gap caused by the free adjustment of the cooling gap height.
  • the free radial displaceability eliminates the need for expensive adjusting devices for manual or automatic radial adjustment of the cooling shells.
  • the elimination of these Anzustell pleaseden also eliminates the problems associated with the prior art in terms of the required space requirements, the time required for the setting or employment and the risks associated with the adjustment for the staff.
  • the accuracy of the adjustment of the size of the cooling gap need not be questioned, because due to the free play of the forces, the size or height of the cooling gap at any time during rolling automatically or automatically optimal.
  • the cooling shell is suspended freely swinging on the single pivot.
  • the freely oscillating suspension of the cooling shell serves, just like the free displacement in the radial direction to the fact that the cooling medium in the cooling gap is not forcibly guided only in the circumferential direction but in the radial direction.
  • the degree of freedom in the radial direction prevents in particular, as I said, the occurrence of undesirable turbulent cross flows at the entrance and at the exit of the cooling gap and thus ensures an always uniform and equal direction flow, whereby a uniform optimal cooling is achieved.
  • the uniform cooling is - when using the role as Roll in a roll stand - an advantageous uniform wear of the rolls and a consistently high quality of the rolling stock.
  • a bay weight is attached to the convexly curved outer side of the cooling shell - optionally also spaced by a lever arm to the outside of the cooling shell.
  • pendulum rudder angle means the position or situation in which the cooling shell would settle with the ballast weights if it were exposed to the weight force alone - suspended in a sympathetic way - the torque represents a certain surface load which acts on the coolant in the cooling gap
  • a desired cooling capacity can be adjusted in the desired manner by providing a certain surface load as a function of the given pressure or volume flow of the cooling medium in the cooling gap.
  • ballast weights are optional and not mandatory.
  • the cooling shell itself has its own mass distribution, which is already determined when manufacturing the cooling shell.
  • the mass distribution of the cooling shell itself can also be designed to be suitable during production with regard to the torque desired in a later application.
  • the device according to the invention has a positioning device which acts on the bearing for positioning the bearing with the cooling shell mounted thereon at a predetermined position, typically one predetermined angular position ⁇ at the periphery of the roll to be cooled.
  • the angular position on the circumference of the roll to be cooled can in principle be chosen arbitrarily between 0 ° ⁇ ⁇ 360 °.
  • the angular position ⁇ also has an influence on the size of the deflection of the cooling shell from the pendulum backrest and thus on the size of the torque and the size of the surface load acting on the cooling medium during rolling operation. The greater the deflection, the greater the torque and the wing loading; and vice versa.
  • the above object of the invention is further achieved by a rolling stand according to claim 8 and by a measuring device according to claim 13.
  • the rolling mill has at least one roller in the form of a roll for rolling rolling and the device according to one of the preceding claims.
  • the measuring device has a roller in the form of a measuring roller and a device according to one of claims 1 to 7.
  • the cooling shell is positioned on the circumference of the roller or roller and stored there freely displaceable in the bearing in the radial direction.
  • the claimed installation site has the advantage that no uneven load between the inlet side and the outlet side of the roll gap is created and that is therefore given here by such uniform load also no negative effects on the roll bending arises.
  • the bearing may have two halves which, with the disadvantages described in the last paragraph, are attached to the chocks of the roller.
  • the rotary joint on which the device according to the invention according to one of claims 1 to 7 is freely suspended swinging, be formed as this spherical joint.
  • the spherical design offers the advantage that the pivot axis of the cooling shell formed by the rotary joint on the drive and operating side would always remain parallel to the roll or measuring roll axis even with an oblique position of the roll in the roll stand or measuring roll. The cooling shell would then follow the roller or the measuring roller and the function of the cooling shell would always be ensured even with an inclination of the roller or the measuring roller.
  • FIG. 1 shows a cross section through the device according to the invention and the mill stand according to the invention;
  • Figure 2 is a supplement to Figure 1;
  • FIG. 3 shows another embodiment for Anordnu
  • Figure 4 shows a first embodiment of the single bearing for the cooling shell
  • Figure 5 shows a second embodiment of the single bearing for the cooling shell.
  • FIG. 1 shows a cross section through the rolling stand according to the invention. From the roll stand, only a roll in the form of a roll 200 is shown for rolling rolling stock 300. The roll rotates in the direction of rotation D.
  • the roll is associated with a device 100 according to the invention on its right side.
  • the device 100 comprises a cooling shell with a cross section in the form of a portion of a circular arc for covering a surface region of the roller 200.
  • a bearing 120 is arranged with a hinge. The bearing is oriented so that its axis of rotation 122 is perpendicular to the circular cross section of the cooling shell 1 10 and parallel to the axis of rotation A of the roller 200.
  • the cooling shell 1 10 is suspended freely swinging.
  • the only bearing with the rotary joint, in which the cooling shell is rotatably mounted, has a degree of freedom in the radial direction r with respect to the circular cross section of the cooling shell or with respect to the axis of rotation A of the roll 200, so that the cooling shell in the bearing 120 in Radial direction r is freely slidably mounted.
  • the bearing is not only designed as a rotary joint, but also as a sliding bearing.
  • FIG. 4 shows a first embodiment of the single bearing 120 of the cooling shell, which consists of two bearing halves 120 - 1, 120 - 2, which are each attached to one of the mounting pieces, ie. H. attached to one of the bearing housings 210-1, 210-2 of the roller 200.
  • Figure 5 shows a second embodiment of the single bearing 120, wherein the bearing is mounted centrally on the cooling shell 1 10.
  • the bearing is by means of a positioning device 140, for example in the form of a hinge or pivot arm 141, z. B. mounted on a Traverse of the mill stand centrally to the roller 200 and hung.
  • the bearing or the swivel joint can be positioned in any desired angular position ⁇ on the circumference U of the roller in both embodiments.
  • a nozzle device is provided for injecting a cooling medium 400 in a cooling gap between the inside At which side or at which edge of the cooling shell 1 10, the nozzle device 130 feeds the cooling medium 400 in the cooling gap depends on the direction of rotation D of the roller and the question of whether a countercurrent cooling or a Mitstromkühlung is desired; in the latter case, the cooling medium 400 flows in the circumferential direction and rotational direction D of the roller 200.
  • this advantageously has no limitation, in particular no collecting container for the cooling medium, so that an unimpeded force-free outflow of the cooling medium is ensured there. This is advantageous for the free play of forces mentioned in the next paragraph.
  • the cooling medium 400 with the nozzle means 130 either a given volume flow V stream or a predetermined pressure P in the
  • Cooling gap pressed into it Due to the freely movable in the radial direction freely rotatable hinge 120 120 arises at a free play of forces, the height h of the cooling gap 160 automatically or automatically optimally. Due to the free swinging suspension of the cooling shell in the pivot joint 120, the height h of the cooling gap is not only automatically at the height of the rotary joint, but everywhere in the angular range ß of the cooling shell automatically or independently properly. A manual or automatic fixed setting of the height h is thus unnecessary.
  • the self-adjusting height h of the cooling gap is, as I said, dependent on the free play of the forces.
  • the gap height is influenced by the following physical variables: the volume flow or the pressure of the cooling medium 400 in the cooling gap and the torque or the resulting surface load, which / which the cooling shell, possibly with attached Baiastmayen, in rolling operation at deflection to the axis of rotation 122 of the rotary joint 120 exerts on the cooling medium.
  • h f [l / ( m * g); 1 / C; V current ; P] (1) where: h: gap height
  • the torque of the cooling shell 1 10 with the ballast weights 1 12 depends on the distribution of the ballast weights 1 12 at the convex outer periphery of the cooling shell 1 10 and their distance from the convex outside of the cooling shell 1 10.
  • the dashed lines symbolize the greater force or torque effect with load weights 1 12 applied further outward than ballast weights lying further inside (not dashed lines).
  • the bearing 120 is designed as a sliding bearing with a radially freely displaceable pivot for free swinging suspension of the cooling shell.
  • typical positioning of the bearing in a certain angular position ⁇ would be fixed to the circumference of the roller.
  • the bearing 120 may be realized by attaching the hinge to the positioning device 140, which is pivotable in a plane transverse to the axis of rotation of the roller 200.
  • the positioning device 140 is shown in Figure 1, only one lever 141, at one end of the pivot 120 is disposed and the other end z.
  • the positioning device 140 may have a drive, not shown in Figure 1 for positioning the rotary joint in an initial position before and at the beginning of the cooling operation.
  • This drive can be mechanical, electromechanical, pneumatic or hydraulic.
  • the drive can be arranged either inside or outside of the roll stand. In the initial position but - at the latest with the beginning of the rolling and cooling operation - the radial free displacement must be guaranteed or allowed.
  • the curvature of the cooling shell 1 10 preferably corresponds to the curvature of the roller 200, so that the center axis of the curved cooling shell 1 10 preferably coincides with the axis of rotation of the roller 200, as indicated in Figure 1 by the dotted lines and the angle ß.
  • a scraper 150 is arranged.
  • This scraper 150 protects the components above it, ie in particular the cooling device 100 according to the invention Before influences of the rolling stock 300. Furthermore, the scraper ensures that the rolling stock 300 is derived from the roller 200 and forwarded in the rolling direction WR.
  • the roll can also be designed as a measuring roll, on the surface of which sensors, typically pressure sensors, are arranged. Such a measuring roller may for example be mounted in a roller table behind a rolling train. During operation, the measuring roll may be partially wrapped by hot rolling, which may cause the sensors to overheat.
  • the device according to the invention can then be positioned on the circumference of the measuring roller for cooling the sensors. In this way, a temperature range can be set at the sensors, which does not affect the sensors.
  • the cooling device according to the invention for cooling a roll in a roll stand or for cooling a measuring roll functions as follows:
  • the size of the The resulting torque also depends on the angular position ⁇ of the rotational axis of the rotary joint 120 on the circumference of the roller, because then depends on the size of the lever arm C, which is the distance between the gravity line of the cooling shell 1 10, when suspended freely swinging at the pivot 120 is (left dash-dotted line in Figures 1 and 2) and upon deflection of the loaded cooling shell due to the roller 200 and the cooling medium 400 in the cooling gap; see right dotted line in Figures 1 and 2.
  • the size of the lever arm C is substantially influenced by the position of the rotary joint 120 on the circumference of the roller 200.
  • the said radial forces due to the torque of the cooling shell 1 10 act towards the center or to the axis of rotation of the roller or roller 200 out.
  • the cooling shell 1 10 is also attracted by the flowing in the cooling gap 160 cooling medium 400 to the axis of rotation of the roller or the roll, because in the cooling gap due to the flowing medium 400, there is a negative pressure.
  • the two said to the axis of rotation of the roller or roller indicative power distributions are compensated in their entirety by a reactive force distribution, which is applied by the cooling medium in the cooling gap, because the cooling medium in the cooling gap can not be compressed in principle and predetermined by the nozzle device 130 Volume flow or pressure of the cooling medium must be taken into account.
  • the radial reaction force distribution prevents the height of the cooling gap from becoming "0."
  • the cooling shell 110 Due to the optionally and variably positionable ballast weights, the cooling shell 110 has an adjustable characteristic with regard to its mass distribution and thus the torque exerted by it 12 is variable in size and can be freely positioned in its distribution on the convex outer side of the cooling shell, and the radian dimension ⁇ can also be suitably selected from the coincidence of the cooling shell mass distribution characteristic with the given volume flow or Pressure of the cooling medium 400 through the nozzle device 130 automatically results in a certain size h of the cooling gap 160.
  • the coincidence of the parameters described causes the cooling shell 1 10 by the adjusting pressure conditions in the cooling medium-flowed cooling gap 160 adhering the cooling shell on the cooling medium 400th or effected on the roller 200.
  • the height h of the cooling gap can be influenced by varying the mass distribution of the ballast weights 1 12 and the angular position ⁇ . Specifically, larger ballast weights or larger torques cause a higher surface load, which ultimately has to be borne by the flow of the cooling medium 400 in the cooling gap 160.
  • the volume flow V ström 0C ' he the pressure P of the cooling medium 400 of the nozzle device 130 in process variables serves predetermined limits of a higher-level control of the rolling process the cooling process are provided.
  • the heat output desired in each case represented by the so-called heat transfer value a, depends on the height h of the cooling gap 160 and the volume flow of the cooling medium 400 in the cooling gap 160.
  • predetermined pressure or flow rate of the cooling medium can be the required torque of the cooling shell 1 10 calculated about the axis of rotation 122. Specifically, the necessary torque then results as the integral of the pressure distribution of the cooling medium 400 in the cooling gap 160 multiplied by the surface of the cooling shell 1 10 integrated over the distance to the suspension point d. H. to the axis of rotation 122 of the bearing 120th
  • the inventively proposed cooling device has the advantage that the height h of the cooling gap 160 automatically optimally adjusted in the radial direction and that the cooling shell floats on the roller or roller or by the flow and pressure conditions of the cooling medium 400 in the cooling gap adheres to the roller.
  • the thus operated cooling device causes a uniform cooling in the circumferential direction and across the width of the roller.
  • FIG. 3 shows a further exemplary embodiment for positioning the cooling device 100 according to the invention on the circumference of the roller 200.
  • FIG. 3 shows an embodiment of the device 100 according to the invention, in which the cooling shell is arranged on the underside of the roller 200 for cooling the roller in the region of the quadrants III and IV.
  • the rotary bearing 120 is fastened to a positioning device 140, which essentially a lever arm 141 which is mounted pivotably about a pivot point 143.
  • the positioning device 140 is designed so that it allows a pivoting of the pivot arm 1 14 at least in an angular range ⁇ , whereby a free displaceability of the rotary joint 120 in the radial direction r is made possible.
  • the cooling shell 1 10 is freely pendulum suspended from the pivot bearing 120;
  • the ballast weight 1 12 in the present case via the lever arm 1 14 so arranged with respect to the axis of rotation 122 of the rotary joint 120 that the cooling shell 1 10 with a total surface load F and a torque M presses against the underside of the roller 200 and not For example, in a gravity line in the direction of the weight, ie in the pendulum soiling falls.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • General Physics & Mathematics (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Metal Rolling (AREA)
  • Control Of Metal Rolling (AREA)

Abstract

L'invention concerne un dispositif et un procédé de refroidissement d'un rouleau. Le rouleau peut être un cylindre d'une cage de laminoir ou un rouleau de mesure. Le dispositif comprend une chemise de refroidissement dont la section transversale a la forme d'une partie d'un arc de cercle destinée à recouvrir une zone de surface du rouleau 200, au niveau d'un bord de la chemise de refroidissement un palier étant formé avec une articulation tournante 120 ayant un axe de rotation qui s'étend perpendiculairement à la section transversale en arc de cercle pour faire pivoter la chemise de refroidissement sur l'axe de rotation. Selon l'invention, pour toujours régler automatiquement de manière optimale la taille de l'espace de refroidissement pendant l'opération de laminage ou pendant le fonctionnement d'un rouleau de mesure, le palier a un degré de liberté dans la direction radiale r par rapport à la section transversale en arc de cercle de la chemise de refroidissement de sorte que la chemise de refroidissement est montée de façon à pouvoir coulisser librement dans le palier dans la direction radiale.
EP15801169.2A 2014-11-27 2015-11-26 Dispositif et procédé de refroidissement d'un rouleau Active EP3223971B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102014224318.1A DE102014224318A1 (de) 2014-11-27 2014-11-27 Vorrichtung und Verfahren zum Kühlen einer Rolle
PCT/EP2015/077843 WO2016083546A1 (fr) 2014-11-27 2015-11-26 Dispositif et procédé de refroidissement d'un rouleau

Publications (2)

Publication Number Publication Date
EP3223971A1 true EP3223971A1 (fr) 2017-10-04
EP3223971B1 EP3223971B1 (fr) 2018-07-04

Family

ID=54705186

Family Applications (1)

Application Number Title Priority Date Filing Date
EP15801169.2A Active EP3223971B1 (fr) 2014-11-27 2015-11-26 Dispositif et procédé de refroidissement d'un rouleau

Country Status (10)

Country Link
US (1) US10967409B2 (fr)
EP (1) EP3223971B1 (fr)
JP (1) JP6527945B2 (fr)
KR (1) KR101978249B1 (fr)
CN (1) CN107000001B (fr)
DE (1) DE102014224318A1 (fr)
MY (1) MY190593A (fr)
RU (1) RU2676363C2 (fr)
UA (1) UA116862C2 (fr)
WO (1) WO2016083546A1 (fr)

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KR20190128859A (ko) 2018-05-09 2019-11-19 주식회사 포스코 압연롤 냉각 장치 및 이를 이용한 압연롤 냉각 방법
DE102019217569A1 (de) * 2019-06-25 2020-12-31 Sms Group Gmbh Planheitsmessvorrichtung zur Messung der Planheit eines metallischen Bandes
DE102020205250B4 (de) * 2020-04-24 2021-11-11 Kocks Technik Gmbh & Co Kg Führungsvorrichtung für Langprodukte
CN112122363A (zh) * 2020-09-10 2020-12-25 宜兴市永昌轧辊有限公司 一种在轧辊冷处理过程中检测其内部冷却到温时间的方法

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DE102009040876A1 (de) * 2008-11-18 2010-05-20 Sms Siemag Ag Vorrichtung zum Kühlen einer Walze in einem Walzgerüst
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DE102011104735A1 (de) * 2011-06-16 2012-12-20 Sms Siemag Ag Verfahren und Vorrichtung zum Kühlen einer Arbeitswalze
DE102012202340A1 (de) 2011-12-23 2013-06-27 Sms Siemag Ag Verfahren und Vorrichtung zum Kühlen von Walzen
DE102012216570A1 (de) 2012-05-11 2013-11-14 Sms Siemag Ag Vorrichtung zum Kühlen von Walzen
JP5939409B2 (ja) 2014-06-06 2016-06-22 株式会社三洋物産 遊技機
WO2017099227A1 (fr) 2015-12-11 2017-06-15 三菱ケミカル株式会社 Résine de polycarbonate aromatique, composition de résine de polycarbonate aromatique, et procédé de fabrication de corps moulé en résine de polycarbonate aromatique

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CN107000001B (zh) 2021-07-02
RU2676363C2 (ru) 2018-12-28
WO2016083546A1 (fr) 2016-06-02
US10967409B2 (en) 2021-04-06
DE102014224318A1 (de) 2016-06-02
KR20170080652A (ko) 2017-07-10
US20180009016A1 (en) 2018-01-11
RU2017122338A (ru) 2018-12-27
JP2018500174A (ja) 2018-01-11
JP6527945B2 (ja) 2019-06-12
UA116862C2 (uk) 2018-05-10
CN107000001A (zh) 2017-08-01
KR101978249B1 (ko) 2019-09-03
RU2017122338A3 (fr) 2018-12-27
EP3223971B1 (fr) 2018-07-04
MY190593A (en) 2022-04-27

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